JP5814807B2 - Rotating seal ring - Google Patents

Description

  The present invention relates to a rotary seal ring. More specifically, the present invention relates to a rotating seal ring that can spread oil in a hydraulic device as a lubricating oil over the entire sealing surface and reduce the amount of oil leakage.

  Various sealing rings for rotation are provided to seal the rotating parts of automobile transmissions, torque converters, hydraulic cylinders, compressors of air conditioning equipment, and other hydraulic equipment. As one of these rotating seal rings, a seal ring provided with a screw-like notch and configured so that the lubricating oil introduced from the screw-like notch is coated on the seal surface (Patent Document 1). And a seal that receives and retains the lubricant by an element having at least one axial end-face cavity that extends radially outward from a radially inner peripheral surface to a position that does not reach the radially outer peripheral surface. A ring (Patent Document 2) has been proposed. However, in these seal rings, the notch does not reach the outer edge, so the lubricating oil does not spread to the outer edge, and the wear on the outer part becomes severe, and the transmission torque due to shortened life and increased sliding resistance of the seal There is a disadvantage that it causes a decrease in In this type of rotating seal ring, a very small amount of oil filled in the hydraulic equipment is used as lubricating oil.

  As a seal ring in which lubricating oil spreads over the entire seal surface, a rotation seal ring provided with a lubrication groove (hereinafter sometimes referred to as a through groove) penetrating from the inner periphery to the outer periphery of the seal surface (Patent Documents 3 to 7) ) Has been proposed. However, in such a seal ring, when the oil pressure in the hydraulic device increases, the amount of oil leaking through the through groove becomes excessive, depending on the number of through grooves.

Japanese Utility Model Publication No. 3-88062 JP 2000-310336 A Japanese Patent Laid-Open No. 9-96363 JP 2001-141065 A JP 2001-295943 A JP 2002-276815 A JP 2007-211702 A

  An object of the present invention is to provide a rotating seal ring that can not only distribute lubricating oil over the entire sealing surface but also reduce the amount of oil leakage.

The present invention is a seal ring in which a plurality of end grooves are provided on at least one side surface, and each end groove has an inner opening that opens on the inner edge side of the seal ring, and another end groove. The end groove has an outer port that opens to the outer edge side of the seal ring, the outer end of the end groove having the inner port is at a distance Ta from the inner edge of the ring, and the inner end of the end groove having the outer port Is at a distance Tb from the outer edge of the ring, and the distance between the outer edge and the inner edge is T:
T <Ta + Tb
Provided is a seal ring for rotation.

In one embodiment, the following formula:
0.6 ≦ Ta / T ≦ 0.9
0.6 ≦ Tb / T ≦ 0.9
Both hold.

In another embodiment, the following formula:
0.2 ≦ (Ta + Tb−T) /T≦0.75
Holds.

  In a further embodiment, the number of end grooves having an inner opening is 0.5 to 2 times the number of end grooves having an outer opening.

  In a further embodiment, the surface having the end groove is further provided with a through groove penetrating the inner edge and the outer edge, and the number of the through grooves is equal to or less than the number of the end grooves having the outer opening.

  According to the present invention, oil is introduced into the inner edge end groove from the inner opening of the end groove having the inner opening (hereinafter, sometimes referred to as an inner edge end groove), and the introduced oil is introduced into the inner edge end groove. The oil supplied from the groove to the sealing surface is collected by the end groove having the outer opening (hereinafter sometimes referred to as the outer edge end groove) and spreads over the entire outer edge end groove. Furthermore, the rotation of the seal ring for rotation eventually spreads the oil over the entire seal surface and functions as a lubricating oil to prevent wear of the seal ring for rotation and suppress a decrease in transmission torque due to an increase in the sliding resistance of the seal. Can do.

  Further, according to the present invention, since the inner edge end groove and the outer edge end groove are separately provided, the end groove having the outer opening even when the number of rotations of the device increases and the oil pressure in the hydraulic device increases. The internal oil pressure does not increase and the amount of oil that leaks does not increase.

It is a schematic explanatory drawing which shows the side surface of the seal ring for rotation of this invention. It is a model explanatory drawing which shows the dimensional relationship of the seal ring for rotation of this invention. It is a schematic explanatory drawing which shows another example of the inner edge end groove in this invention. It is a schematic explanatory drawing which shows another example of the outer edge end groove | channel in this invention. It is a schematic explanatory drawing which shows another example of the seal ring for rotation. It is a schematic explanatory drawing which shows the further another example of the seal ring for rotation. It is a schematic explanatory drawing which shows the oil stop hole applicable to the seal ring for rotation of this invention. It is a schematic explanatory drawing which shows the state which combined the end groove | channel and oil stop hole in this invention.

  The rotational seal ring 1 of the present invention is for sealing lubricating oil at the rotational portion of a torque converter or other hydraulic equipment. As shown in FIG. 1, at least one axial side surface (preferably both side surfaces) ) Is provided with a plurality of end grooves 2. In addition, one of the end grooves 2 (inner edge end groove 2 i) has an inner port 2 i 1 that opens to the inner edge side of the seal ring, and another end groove 2 (outer edge end groove 2 o) is outside the seal ring. It is configured to have an outer opening 2o1 opening on the edge side.

  The end groove 2 in the present invention takes in a very small amount of oil in the hydraulic equipment and makes it a lubricating oil, and spreads over the entire surface (hereinafter sometimes referred to as a sealing surface) where the seal ring and the hydraulic equipment are in contact with each other. This is to prevent a decrease in transmission torque due to an increase in the sliding resistance of the sealing while preventing wear of the rotating seal ring 1. Although the structure having the same function is a through groove, the end groove 2 in the present invention is different from the through groove 3, and the end groove 2 having the inner port 2i1 does not have the outer port 2o1, but has the outer port 2o1. Since the end groove 2 does not have the inner port 2i1, even when the hydraulic pressure in the hydraulic device rises, the large hydraulic pressure applied to the inner port 2i1 is not directly transmitted to the outer port 2o1, so oil leakage is prevented. Can be suppressed.

  In a normal case, the inner edge end groove 2i and the outer edge end groove 2o are provided at a ratio of 1: 1. However, since the lubricating oil tends to be insufficient in the vicinity of the outer edge in the present invention, the number of outer edge end grooves 2o may be increased to twice that of the inner edge end grooves 2i in order to compensate for this. In addition, when it exceeds 2 times, the sealing property tends to deteriorate.

  Further, from the viewpoint of preventing oil leakage, the number of outer edge end grooves 2o may be reduced to 0.5 times the number of inner edge end grooves 2i. In addition, when it is less than 0.5 times, there is a tendency that wear becomes intense or seizure tends to occur near the outer edge.

  In the case of the seal ring 1 having severe conditions such as for high-speed rotation, it is necessary to increase the amount of lubricating oil on the seal surface in accordance with the conditions. In such a case, since the shortage of lubricating oil becomes significant on the outer edge side of the seal ring, the lubricating oil may be supplemented by using the through groove 3 in addition to the end groove 2. However, since the oil leakage increases when the number of the through grooves 3 is large, it is preferable that the number of the through grooves 3 does not exceed the number of the outer edge-ended grooves 2o. In addition, when providing the penetration groove | channel 3, it is preferable that the position to provide is made into the position which equally divides the center angle of a seal ring.

  The depth and width of the above-mentioned end groove 2 and through groove 3 may be the same as the through groove in the conventional rotary seal ring. Specifically, the depth is about 0.1 to 0.5 mm and the width is about About 0.2-1.0 mm is preferable.

As schematically shown in FIG. 2, the rotary seal ring 1 of the present invention has an outer end 2i2 of the inner edge end groove 2i at a distance Ta from the inner edge 4 of the ring, and an inner end 2o2 of the outer edge end groove 2o. Is at a distance Tb from the outer edge 5 of the ring and the distance between the outer edge 5 and the inner edge 4 is T:
T <Ta + Tb
It is characterized by that. However, in FIG. 2, in order to clearly indicate the lengths indicated by T, Ta, and Tb, the distance between the outer edge and the inner edge is extremely widened. Note that Ta is not the length of the inner edge-ended groove 2i, but precisely the length of the vertical line when the vertical line is drawn from the outer end 2i2 of the inner edge-ended groove 2i toward the inner edge 4, that is, in the radial direction. Length. Similarly, Tb is not the length of the outer edged groove 2o, but precisely the length of the vertical line when the vertical line is drawn from the inner end 2o2 of the outer edged groove 2o toward the outer edge 5, ie, in the radial direction. Is the length of

  This type of rotating seal ring is sandwiched between the rotating shaft of the hydraulic device and the casing and is in pressure contact with the inner periphery of the casing by the fluid pressure, and the seal ring has both the rotating shaft and the casing while the rotating shaft is rotating. Rotating motion with respect to The rotating seal ring 1 of the present invention is also rotated in the same manner. However, in the case of the present invention, since it has an end groove 2i (inner edge end groove 2i) having an inner opening on the inner edge side, the inner edge end groove 2i. Oil is applied to the sealing surface of the hydraulic device, and the applied oil adheres to the surface of the seal ring 1 and acts as a lubricating oil. Therefore, the lubricating oil is used from the inner edge 4 of the seal ring 1 to the distance Ta. Will be applied.

  Here, in the present invention, T <Ta + Tb is satisfied, that is, the inner end 2o2 of the outer edge end groove 2o is in the range where the above-described lubricating oil is applied, and therefore the inner end 2o2 of the outer edge end groove 2o. Lubricating oil is scraped in the area. The lubricating oil once scraped spreads inside the outer edged end groove 2o, then enters between the seal ring 1 and the hydraulic device, and again acts as lubricating oil.

  Since the lubricating oil is scraped up by the outer edge-ended groove 2o, a portion of the seal surface through which both the inner edge-ended groove 2i and the outer edge-ended groove 2o pass (a portion indicated by hatching in FIG. 2). In this overlapping portion O, the lubricating oil is quickly replenished when the inner edge end groove 2i passes through this portion.

  In the present invention, as shown in FIG. 3, the inner edge end groove 2i may be (a) extending from the inner edge 4 toward the centrifugal direction, or (b) a direction inclined toward the rotational direction side. (C) It may be inclined and extended in the direction opposite to the rotation direction. In FIG. 3, the white arrow indicates the rotation direction of the seal ring 1 relative to the hydraulic device.

  In the normal case, the inner edge end groove 2i is extended in the centrifugal direction as shown in (a). However, in the case where excessive oil enters the sealing surface, for example, when the hydraulic pressure in the hydraulic device is high (b) The oil may be repelled inward by using the rotation of the seal ring by tilting as shown in (), or conversely, when the hydraulic pressure is low, the seal ring is rotated by tilting as shown in (c). You may make it introduce | transduce oil into a sealing surface using. In FIG. 3, each of the inner end-ended grooves 2i has a linear shape, but may have a curved shape, a wave shape, a square shape, a zigzag shape, or the like, or a bent line shape combining these.

  In the present invention, as shown in FIG. 4, the outer edge end groove 2 o may be (a) extending from the outer edge 5 toward the centripetal direction, or (b) a direction inclined toward the rotational direction side. (C) It may be inclined and extended in the direction opposite to the rotation direction. In FIG. 4, the white arrow indicates the rotation direction of the seal ring 1 relative to the hydraulic device.

  In the normal case, the outer edge end groove 2o is extended in the centripetal direction as shown in (a). However, when the oil pressure in the hydraulic device is low, the lubricating oil tends to be insufficient in the vicinity of the outer edge (b). In this case, the oil may be introduced to the outside by using the rotation of the seal ring, or when the seal surface has too much oil, the seal ring is rotated as shown in (c). The oil may be repelled inward to prevent oil leakage. In FIG. 4, the outer edge end groove 2o has a linear shape, but can have various shapes as with the inner edge end groove 2i.

  In the present invention, the inner edged groove 2i and the outer edged groove 2o can be arranged in various combinations as long as they are arranged so as to have overlapping portions (that is, so as to satisfy the formula: T <Ta + Tb). For example, as shown in FIG. 5, the overlapping portion may be arranged near the outer edge 5 of the seal ring 1, or as shown in FIG. 6, the overlapping portion is near the inner edge 4 of the seal ring 1. You may arrange in. In addition, as shown in FIG. 5, when the length of the inner edge end groove 2i is made longer than the outer edge end groove 2o, the inner edge end groove 2i is completely filled with lubricating oil. On the other hand, the scraped amount of the lubricating oil by the outer edged groove 2o becomes unstable, and the lubricating oil tends to be excessive or insufficient on the outer peripheral side.

  However, it is preferable that the lengths of Ta and Tb satisfy the formula: 0.6 ≦ Ta / T ≦ 0.9 and the formula: 0.6 ≦ Tb / T ≦ 0.9. When Ta / T and Tb / T are smaller than 0.6, there are few overlapping portions, which may cause inconvenience of insufficient lubrication. When it is larger than 0.9, the outer edge or inner edge tends to be damaged, and that portion. Oil may easily leak from the tank.

  The value of (Ta + Tb−T) / T, that is, the ratio of the width (Ta + Tb−T) of the overlapping portion O to the width (T) of the seal ring 1 is determined by the fact that the oil that functions as the lubricating oil passes through the seal surface through the inner edge end groove 2i. Is not particularly limited as long as it can be transferred to the outer edge end groove 2o, but is preferably about 0.2 to 0.75. If the value of (Ta + Tb-T) / T is smaller than 0.2, the oil from the inner edge groove 2i to the outer edge groove 2o when the oil viscosity is high or the oil pressure is low, etc. , And there is a case where the lubricating oil is insufficient at the outer edge 5 portion and wear or the like becomes severe. On the other hand, if it is larger than 0.75, the amount of oil leakage increases, and there may be a disadvantage that it takes time to increase the hydraulic pressure.

  In addition, the rotation seal ring 1 of the present invention can be provided with a structure used in a conventional seal ring as long as the effects of the present invention are not impaired. For example, a normal seal ring or piston ring is provided with an abutment for securing the mounting property to a piston or rotating shaft or absorbing a dimensional change due to a temperature change, as shown in FIG. An abutment 7 is also provided in the seal ring 1 of the present invention.

  Moreover, in order to reduce the amount of oil leakage, the conventional rotation seal ring 1 has an oil stop hole 6 including a concave portion 6a and a through hole 6b as shown in FIG. However, the oil stop hole 6 can also be provided in the seal ring 1 of the present invention. When the oil stop hole 6 is provided, it may be provided separately from the end groove 2 of the present invention, or may be provided in combination as shown in FIG.

  As the material for the rotation seal ring 1 of the present invention, all materials used for ordinary seal rings can be suitably used. Specifically, a high-performance engineering plastic in which a filler is blended with PTFE, PEEK, polyimide, or the like. It can be illustrated. Examples of the filler include copper powder, molybdenum dioxide, glass fiber, and carbon fiber, and these can be used alone or in combination of two or more.

  The rotating seal ring of the present invention has an inner opening in which one of the end grooves opens on the inner edge side of the seal ring, and an outer opening in which another end groove opens on the outer edge side of the seal ring. And the outer end of the end groove having the inner opening is at a distance Ta from the inner edge of the ring, and the inner end of the end groove having the outer opening is at a distance Tb from the outer edge of the ring, between the outer edge and the inner edge. Since the formula: T <Ta + Tb holds when the distance is T, it is used in the field of hydraulic equipment such as a torque converter. In particular, it is useful in fields where it is necessary to prevent oil leakage while supplying a necessary amount of oil as a lubricating oil to the sealing surface.

1 Rotating Seal Ring 2 Ended Groove 2i Ended Groove with Inner Port (Inner Edge Ended Groove)
2i1 Inner port 2i2 Outer end 2o Ended groove with outer port (outer edge end groove)
2o1 Outer port 2o2 Inner end 3 Through groove 4 Inner edge 5 Outer edge 6 Oil stop 6a Recessed portion 6b Through hole 7 Mating point T Distance between inner edge and outer edge (width of seal ring)
Ta Distance between inner edge and outer edge Tb Distance between outer edge and inner edge O Overlapping part

Claims (4)

A seal ring provided with a plurality of end grooves on at least one side surface,
One of the end grooves has an inner opening that opens on the inner edge side of the seal ring, and the other end groove has an outer opening that opens on the outer edge side of the seal ring,
The outer end of the end groove with the inner opening is at a distance Ta from the inner edge of the ring,
The inner end of the end groove with the outer opening is at a distance Tb from the outer edge of the ring;
When the distance between the outer edge and the inner edge is T:
T <Ta + Tb
Start-Chi, and is made
A rotation seal ring in which a through groove that penetrates the inner edge and the outer edge is further provided on the surface having the end groove, and the number of the through grooves is equal to or less than the number of the end grooves having the outer opening . The following formula:
0.6 ≦ Ta / T ≦ 0.9
0.6 ≦ Tb / T ≦ 0.9
The rotating seal ring according to claim 1, wherein both hold. The following formula:
0.2 ≦ (Ta + Tb−T) /T≦0.75
The rotation seal ring according to claim 1, wherein:   The rotation seal ring according to any one of claims 1 to 3, wherein the number of the end grooves having the inner opening is 0.5 to 2 times the number of the end grooves having the outer opening.

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